CN111032564A - Control valve - Google Patents
Control valve Download PDFInfo
- Publication number
- CN111032564A CN111032564A CN201780093986.3A CN201780093986A CN111032564A CN 111032564 A CN111032564 A CN 111032564A CN 201780093986 A CN201780093986 A CN 201780093986A CN 111032564 A CN111032564 A CN 111032564A
- Authority
- CN
- China
- Prior art keywords
- region
- valve body
- mast
- opening area
- flow path
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0708—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides comprising means to avoid jamming of the slide or means to modify the flow
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/08—Masts; Guides; Chains
- B66F9/10—Masts; Guides; Chains movable in a horizontal direction relative to truck
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/07559—Stabilizing means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/20—Means for actuating or controlling masts, platforms, or forks
- B66F9/22—Hydraulic devices or systems
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Civil Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Forklifts And Lifting Vehicles (AREA)
Abstract
The cutout portion 41 formed in the shoulder portion 31 of the main spool 30 for blocking the communication between the extension-side actuator port a and the second flow path T includes: a first cut-out portion and a second cut-out portion. The first incision portion includes: a first region in which the opening area between the valve body 40 and the shoulder portion 31 gradually increases and which has a semicircular shape in plan view; and a second region which is provided continuously with the first region and in which an opening area between the valve body 40 and the shoulder portion 31 is fixed, the second cutout portion including: a third region in which the opening area between the valve body 40 and the shoulder portion 31 gradually increases and which is semicircular in plan view; and a fourth region that is provided continuously with the third region and has a fixed opening area between the valve body 40 and the shoulder portion 31.
Description
Technical Field
The present invention relates to a control valve that is connected to a hydraulic cylinder for moving a mast for raising and lowering a fork forward and backward in a Reach fork lift (Reach fork).
Background
The forward forklift has the following structure: a mast that can be used to raise and lower a fork is moved in the front-rear direction between an extended (reach in) state, which is a pulled-in state, and an extended (reach out) state, which is a forward extended state.
In this type of forward forklift, a control valve connected to a hydraulic cylinder for moving a mast is configured as follows: by moving the spool (spool) relative to the valve body, a first flow path for introducing hydraulic oil at a high pressure and a second flow path that opens to a low-pressure region are selectively connected to an extension-side actuator port for urging the piston toward a side for moving the mast forward and an extension-side actuator port for urging the piston toward a side for moving the mast rearward. In such a control valve, the flow rate of the hydraulic oil is controlled by a notch portion (concave portion) formed in the shoulder portion of the spool.
In such a forward forklift, when the forward lever is operated to the extension side in a state of traveling while supporting the workpiece, a force is generated by an inertial force to move the mast in the traveling direction of the vehicle body when the forward forklift is suddenly braked. Since the force is transmitted to the hydraulic cylinder, the force for limiting the position of the mast in the front-rear direction by the hydraulic cylinder becomes unstable, and a phenomenon occurs in which the mast and the fork supported by the mast become unstable.
[ Prior art documents ]
[ patent document ]
[ patent document 1] Japanese patent laid-open No. 2000-53398
Disclosure of Invention
[ problems to be solved by the invention ]
The forward movement control device described in patent document 1 requires not only a flow rate adjustment valve but also a vehicle speed detection member and a load detection member, and therefore has the following problems: the apparatus is expensive, complicated in structure, and difficult to control.
The present invention has been made to solve the above problems, and an object of the present invention is to provide a control valve which has a simple structure and can stabilize a mast even when a forward forklift is suddenly braked during an extending operation.
[ means for solving problems ]
The invention described in claim 1 is a control valve that is connected to a hydraulic cylinder for moving a mast for raising and lowering a fork forward and backward in a forward forklift, wherein the controller selectively connects a first flow path for introducing high-pressure hydraulic oil and a second flow path that opens to a low-pressure region to an extension-side actuator port for applying a force to a side where a piston of the hydraulic cylinder moves the mast forward and an extension-side actuator port for applying a force to a side where the piston of the hydraulic cylinder moves the mast backward by moving a spool relative to a valve body by moving the spool relative to the valve body, wherein a cutout portion formed in a shoulder portion of the spool is formed in a shape in which an opening area formed between the valve body and the shoulder portion changes in two stages, the shoulder portion is to block communication of the reach-side actuator port with the second flow path.
The invention of claim 2 is the invention of claim 1, wherein a cutout portion formed in a shoulder portion of the spool for blocking communication between the insertion-side actuator port and the second flow passage is formed in a shape in which a distance between the valve body and the shoulder portion changes in at least two stages.
The invention described in claim 3 is the invention described in claim 1, wherein the cutout portion formed in the shoulder portion of the spool for blocking communication between the extension-side actuator port and the second flow path includes: a first region in which an opening area between the valve body and the shoulder portion is gradually increased; a second region which is provided continuously from the first region and in which an opening area between the valve body and the shoulder portion is fixed; a third region which is provided continuously with the second region and in which an opening area between the valve body and the shoulder portion gradually increases; and a fourth region that is provided continuously with the third region, and has a fixed opening area between the valve body and the shoulder portion, a distance between a surface of the first region and a surface of the second region and the valve body being set to a first distance, a distance between a surface of the second region and a surface of the third region and the valve body being set to a second distance that is greater than the first distance, and the first region and the third region having a semicircular shape in plan view.
[ Effect of the invention ]
According to the inventions described in claims 1 to 3, since the cutout portion formed in the shoulder portion of the spool for blocking the communication between the extension-side actuator port and the second flow path is formed in a shape in which the opening area formed between the valve body and the shoulder portion changes in two stages, the mast can be stabilized even when the reach-out forklift is subjected to emergency braking by the action of the cutout region having a small opening area during the extension operation. Further, the movement of the mast can be performed at a high speed by the action of the cutout region having the large opening portion, and the load of the pump for supplying the hydraulic oil can be reduced to suppress the amount of power consumption.
According to the invention described in claim 3, the first region, the second region, the third region, and the fourth region can be easily processed.
Drawings
Fig. 1 is a schematic diagram of a reach truck 10 to which a control valve 20 of the present invention is applied.
Fig. 2 is a cross-sectional view of the control valve 20 of the present invention.
Fig. 3 is a cross-sectional view of the control valve 20 of the present invention.
Fig. 4 is a cross-sectional view of the control valve 20 of the present invention.
Fig. 5 is a plan view showing the relationship between the cut-out portion 41 formed in the shoulder portion 31 of the master spool 30 and the valve body 40.
Fig. 6 is a vertical cross-sectional view showing a relationship between the cut-out portion 41 formed in the shoulder portion 31 of the master spool 30 and the valve body 40, which is shown as a reference example.
Fig. 7 is a table showing the relationship between the position of the main spool 30 and the opening area formed between the valve body 40 and the land portion 31, the land portion 32, the shoulder portion 33, the land portion 34, and the land portion 35 by the notch portion 41, the notch portion 42, the notch portion 43, the notch portion 44, the notch portion 45, the notch portion 46, and the like at this time.
Fig. 8 is an enlarged view of an opening area portion between the valve body 40 and the shoulder portion 31 formed in the hydraulic oil flow path from the inlet-side actuator port a to the second flow path T in fig. 7.
Fig. 9 is a plan view showing the relationship between the cut-out portion 41 formed in the shoulder portion 31 of the master spool 30 and the valve body 40.
Fig. 10 is a vertical cross-sectional view showing the relationship between the cut-out portion 41 formed in the shoulder portion 31 of the master cylinder 30 and the valve body 40.
Fig. 11 is a table showing the relationship between the position of the main spool 30 and the opening area formed between the valve body 40 and the land portion 31, the land portion 32, the shoulder portion 33, the land portion 34, and the land portion 35 by the notch portion 41, the notch portion 42, the notch portion 43, the notch portion 44, the notch portion 45, the notch portion 46, and the like at this time.
Fig. 12 is an enlarged view of an opening area portion between the valve body 40 and the shoulder portion 31 formed in the hydraulic oil flow path from the inlet-side actuator port a to the second flow path T in fig. 11.
Detailed Description
Hereinafter, embodiments of the present invention will be described based on the drawings. First, the configuration of the reach truck 10 to which the control valve 20 of the present invention is applied will be described. Fig. 1 is a schematic diagram of a reach truck 10 to which a control valve 20 of the present invention is applied.
The reach truck 10 is of the type: the mast 12 can be moved in the front-rear direction between an extended state, which is a retracted state, and an extended state, which is a forward extended state, and the mast 12 is used to raise and lower the forks 11 supporting the workpiece. The reach truck 10 includes: a main body 13 provided with front wheels 14 and rear wheels 15; a steering device 16; and a lever 17 for performing various operations. A hydraulic cylinder 18 is disposed at a lower portion of the main body 13, and the hydraulic cylinder 18 moves the mast 12 for raising and lowering the fork 11 in the front-rear direction.
Next, the structure of the control valve 20 of the present invention will be described. Fig. 2 is a cross-sectional view of the control valve 20 of the present invention. In this figure, the main spool 30 is shown in a state of being disposed at an intermediate position.
The control valve 20 is connected to a hydraulic cylinder 18 for moving the mast 12 forward and backward, and the mast 12 is used for raising and lowering the forks 11. The control valve 20 selectively connects a first flow path P for introducing high-pressure hydraulic oil from the hydraulic pump and a second flow path T opening to a low-pressure region such as a hydraulic tank to an extension-side actuator port a for urging the piston 19 of the hydraulic cylinder 18 to a side where the mast 12 moves backward and an extension-side actuator port B for urging the piston 19 of the hydraulic cylinder 18 to a side where the mast 12 moves forward.
The control valve 20 includes a main spool 30, and the main spool 30 is formed with a plurality of shoulder portions 31, 32, 33, 34, 35, and a plurality of groove portions 36, 37, 38, 39 alternately, and is capable of reciprocating in the left-right direction shown in fig. 2 with respect to a valve body 40. The right end of the main spool 30 is connected to the rod 17 shown in fig. 1.
A cutout portion 41(a → T) is formed in the land portion 31, the cutout portion 41(a → T) being used when the hydraulic oil flows from an extension-side actuator port a for biasing the piston 19 of the hydraulic cylinder 18 to a side for moving the mast 12 rearward to a second flow path T that is open to a low pressure region such as a hydraulic tank. The cutout portion 41 is a cutout region also referred to as a notch (notch). When the hydraulic oil is caused to flow from the inlet-side actuator port a to the second flow path T, when the state where the flow of the hydraulic oil is prevented by the shoulder portion 31 is once shifted to the state where the flow of the hydraulic oil is allowed by the groove portion 36, an impact is generated on the control valve 20 by the action of the high-pressure hydraulic oil. Therefore, by causing the hydraulic oil to flow through the cutout portion 41, the occurrence of such an impact is prevented.
For the same reason, the land portion 32 is formed with a notch portion 42(P → a) and a notch portion 43(P → T), the notch portion 42(P → a) being used when the hydraulic oil is caused to flow from the first flow path P to the extension-side actuator port a, and the notch portion 43(P → T) being used when the hydraulic oil is caused to flow from the first flow path P to the second flow path T. Further, a notch portion 44(P → T) used when the hydraulic oil is caused to flow from the first flow path P to the second flow path T, and a notch portion 45(P → B) used when the hydraulic oil is caused to flow from the first flow path P to the extension-side actuator port B are formed in the land portion 34. Further, a cutout portion 46(B → T) is formed in the land portion 35, and the cutout portion 46(B → T) is used when the hydraulic oil is caused to flow from the extension-side actuator port B to the second flow path T.
Next, the operation of the control valve 20 of the present invention will be described. Fig. 3 and 4 are sectional views of the control valve 20 for explaining the operation of the control valve 20 according to the present invention. In the drawings, the workpiece W, the fork 11, the mast 12, the hydraulic cylinder 18, and the control valve 20 are schematically illustrated. Here, fig. 3 shows a state in which the main spool 30 is disposed at a left position, and fig. 4 shows a state in which the main spool 30 is disposed at a right position.
As shown in fig. 2, in a state where the main spool 30 is disposed at the intermediate position, the extending-side actuator port a for biasing the piston 19 of the hydraulic cylinder 18 to the side for moving the mast 12 rearward, the extending-side actuator port B for biasing the piston 19 of the hydraulic cylinder 18 to the side for moving the mast 12 forward, the first flow path P for introducing high-pressure hydraulic oil from the hydraulic pump, and the second flow path T for opening to a low-pressure area such as a hydraulic tank are blocked by the action of the plurality of shoulders 31, 32, 33, 34, and 35 of the main spool 30. Therefore, the pressure feeding of the hydraulic oil to the hydraulic cylinder 18 is not performed.
From this state, when the operator operates the lever 17 shown in fig. 1 to move the main spool 30 connected to the lever 17 to the left as shown in fig. 3, a passage of the hydraulic oil from the first flow path P into which the high-pressure hydraulic oil is introduced to the extension-side actuator port B is formed by the action of the notch portion 45 and the groove portion 39. Further, by the action of the notch portion 41, a passage of the hydraulic oil from the inlet side actuator port a to the second flow path T which is open to a low pressure region such as a hydraulic tank is formed. As a result, the hydraulic oil flows as indicated by the arrow in fig. 3, the piston 19 of the hydraulic cylinder 18 moves to the left as viewed in fig. 3, and the mast 12 for raising and lowering the fork 11 is in an extended state in which it moves forward from the main body 13 side.
On the other hand, according to the state shown in fig. 2, when the operator operates the lever 17 shown in fig. 1 to move the main spool 30 connected to the lever 17 to the right as shown in fig. 4, a passage of the hydraulic oil from the first flow path P into which the high-pressure hydraulic oil is introduced to the inlet-side actuator port a is formed by the action of the notch portion 42 and the groove portion 36. Further, by the action of the notch portion 46 and the groove portion 39, a passage of the hydraulic oil from the extension-side actuator port B to the second flow passage T opened to the low pressure region such as the hydraulic tank is formed. As a result, the hydraulic oil flows as indicated by the arrows in fig. 4, and the piston 19 of the hydraulic cylinder 18 moves to the right side as shown in fig. 4, and the mast 12 for raising and lowering the fork 11 is in an extended state moving to the main body 13 side.
In such a control valve 20, when the operator operates the lever 17 shown in fig. 1 in a state where the workpiece W is supported by the fork 11 and thereby the mast 12 for raising and lowering the fork 11 is in an extended state moving forward from the main body 13 side, the reach truck 10 may be suddenly braked. In this case, due to the inertial force to the workpiece W, the fork 11, and the mast 12, a force is generated by which the mast 12 moves in the traveling direction of the vehicle body away from the main body 13. Since the force is transmitted to the hydraulic cylinder 18, the pressure of the hydraulic oil in the hydraulic cylinder 18 is lowered, and the force for limiting the position of the mast 12 in the front-rear direction by the hydraulic cylinder 18 becomes unstable, whereby the mast 12, the fork 11 supported by the mast 12, and the workpiece W become unstable.
The aspects are explained in further detail. Fig. 5 is a plan view showing a relationship between the cut-out portion 41 formed in the shoulder portion 31 of the main spool 30 and the valve body 40, which is shown as a reference example. Fig. 6 is a vertical cross-sectional view showing a relationship between the cut-out portion 41 formed in the shoulder portion 31 of the master spool 30 and the valve body 40, which is shown as a reference example. Fig. 7 is a table showing the relationship between the position of the main spool 30 and the opening area formed between the valve body 40 and the land portion 31, the land portion 32, the shoulder portion 33, the land portion 34, and the land portion 35 by the notch portion 41, the notch portion 42, the notch portion 43, the notch portion 44, the notch portion 45, the notch portion 46, and the like at this time.
Fig. 8 is an enlarged view of the opening area portion between the valve body 40 and the land portion 31 in the hydraulic oil flow path from the inlet side actuator port a to the second flow path T, which is formed by the notch portion 41 shown in fig. 5 and 6, of fig. 7. In fig. 7 and 8, the horizontal axis represents the movement distance of the main spool 30, and the vertical axis represents the opening area (square mm).
For example, as shown by the broken line in fig. 8, when the opening area between the valve body 40 and the shoulder portion 31 formed by the notch portion 41 in the hydraulic oil flow path from the extension-side actuator port a to the second flow path T is set large, when the mast 12 is set to the extended state as described above, the mast 12, the forks 11 supported by the mast 12, and the workpiece W are in an unstable state when the reach truck 10 is subjected to emergency braking. In contrast, as shown by hatching in fig. 8, when the opening area between the valve body 40 and the shoulder portion 31 formed by the notch portion 41 in the hydraulic oil flow path from the inlet-side actuator port a to the second flow path T is set small, the degree of instability of the mast 12 is reduced.
However, when the opening area between the valve body 40 and the land portion 31 formed by the notch portion 41 in the hydraulic oil flow path from the inlet-side actuator port a to the second flow path T is set small, the flow rate of the hydraulic oil passing through the opening area region becomes small, and therefore, when the extending operation is performed, there is a problem that the forward movement speed of the fork 11 becomes small.
When the opening area between the valve body 40 and the land portion 31 formed in the hydraulic oil flow path from the extension-side actuator port a to the second flow path T by the notch portion 41 is set small, the pressure of the hydraulic oil supplied to the hydraulic cylinder 18 when the extension operation is performed by the rod 17 increases, and the power consumption for driving the hydraulic pump that supplies the hydraulic oil increases. Therefore, a problem of early battery consumption occurs.
Therefore, in the control valve 20 of the present invention, the cutout portion 41 formed in the shoulder portion 31 of the main spool 30 for blocking the communication between the extension-side actuator port a and the second flow path T is formed in the following shape: the opening area formed between the valve body 40 and the shoulder portion 31 is changed in two stages, thereby solving the problem.
Fig. 9 is a plan view showing a relationship between the cut-out portion 41 formed in the shoulder portion 31 of the main spool 30 and the valve body 40 in the control valve 20 of the present invention. Fig. 10 is a vertical cross-sectional view showing a relationship between the cut-out portion 41 formed in the shoulder portion 31 of the main spool 30 and the valve body 40 in the control valve 20 of the present invention. Fig. 11 is a table showing the relationship between the position of the main spool 30 and the opening area formed between the valve body 40 and the land portion 31, the land portion 32, the shoulder portion 33, the land portion 34, and the land portion 35 by the notch portion 41, the notch portion 42, the notch portion 43, the notch portion 44, the notch portion 45, the notch portion 46, and the like at this time. Fig. 12 is an enlarged view of the opening area portion between the valve body 40 and the land portion 31 in the hydraulic oil flow path from the inlet side actuator port a to the second flow path T, which is formed by the notch portion 41 shown in fig. 9 and 10, of fig. 11. In fig. 11 and 12, the horizontal axis represents the movement distance of the main spool 30, and the vertical axis represents the opening area (square mm).
As shown in the above figures, in the control valve 20 of the present invention, the notch portion 41 of the land portion 31 formed in the main spool 30 to block the communication between the extension-side actuator port a and the second flow path T is formed in a shape in which the distance between the valve body 40 and the surface of the notch portion 41 changes in two stages by including the first notch portion 41a and the second notch portion 41 b.
More specifically, the first cut-out portion 41a of the cut-out portion 41 includes a first region, and the opening area between the valve body 40 and the shoulder portion 31 gradually increases and is semicircular in plan view; and a second region provided continuously from the first region and having a fixed opening area between the valve body 40 and the shoulder portion 31, and including, for a second cutout portion 41b of the cutout portion 41: a third region in which the opening area between the valve body 40 and the shoulder portion 31 gradually increases and which is semicircular in plan view; and a fourth region which is provided continuously with the third region and in which the opening area between the valve body 40 and the shoulder portion 31 is fixed, wherein the distance between the surface of the first region and the surface of the second region and the valve body 40 is set to a first distance, and the distance between the second region and the third region and the valve body 40 is set to a second distance greater than the first distance.
With such a configuration, during a normal extension operation, the extension-side actuator port a and the second passage T communicate with each other using the first notch portion 41a, whereby the opening area between the valve body 40 and the land portion 31 formed in the hydraulic oil passage from the extension-side actuator port a to the second passage T can be reduced. This can restrict the flow rate of the hydraulic oil flowing out from the extension-side actuator port a to the second flow path T, and reduce the degree of instability of the mast 12 even when the reach truck 10 is suddenly braked when the mast 12 is in the extended state.
On the other hand, during normal operation, the second notch portion 41b is used to communicate the extension-side actuator port a with the second flow path T, so that the opening area between the valve body 40 and the land portion 31 formed in the hydraulic oil flow path from the extension-side actuator port a to the second flow path T can be set large. This prevents the fork 11 from moving forward at a reduced speed when the extension operation is performed.
Further, since the opening area between the valve body 40 and the land portion 31 formed in the hydraulic oil flow path from the extension-side actuator port a to the second flow path T by the cutout portion 41 can be set large, the pressure of the hydraulic oil supplied to the hydraulic cylinder 18 when the extension operation is performed by the rod 17 does not increase, and the power consumption for driving the hydraulic pump that supplies the hydraulic oil does not increase. Therefore, the battery consumption can be reduced.
In the above embodiment, the first cut-out portion 41a of the cut-out portion 41 includes a first region, and the opening area between the valve body 40 and the shoulder portion 31 is gradually increased and has a semicircular shape in plan view; and a second region provided continuously from the first region and having a fixed opening area between the valve body 40 and the shoulder portion 31, and including, for a second cutout portion 41b of the cutout portion 41: a third region in which the opening area between the valve body 40 and the shoulder portion 31 gradually increases and which is semicircular in plan view; and a fourth region that is provided continuously with the third region and has a fixed opening area between the valve body 40 and the shoulder portion 31. By adopting such a shape, the first notch portion 41a and the second notch portion 41b can be formed in two steps by milling using an end mill (end mill). Therefore, the notch 41 can be easily lowered at low cost.
In the above embodiment, the cutout portion 41 formed in the shoulder portion 31 of the main spool 30 for blocking the communication between the insertion-side actuator port a and the second flow passage T is formed in the following shape: the distance between the valve body 40 and the surface of the cutout portion 41 changes in two stages. However, the opening area formed between the valve body 40 and the shoulder portion 31 may be changed in two stages by changing the dimension of the notch portion 41 in the width direction.
[ description of symbols ]
10: forward type forklift
11: fork
12: mast
18: oil hydraulic cylinder
19: piston
30: main valve column
31: shoulder part
40: valve body
41: cut-out part
41 a: first incision part
41 b: second cut portion
A: reach side actuator port
B: extension side actuator port
P: first flow path
T: a second flow path.
Claims (3)
1. A control valve for a forward forklift, the control valve being connected to a hydraulic cylinder for moving a mast forward and backward, the mast being used to raise and lower a fork, the control valve being configured to selectively connect a first flow path for introducing high-pressure hydraulic oil and a second flow path that opens to a low-pressure region to an extension-side actuator port for applying a force to a side of a piston of the hydraulic cylinder that moves the mast forward and an extension-side actuator port for applying a force to a side of the piston of the hydraulic cylinder that moves the mast backward by moving the mast by moving a spool relative to a valve body, the control valve being configured to move a valve rod to move the mast forward and to move the mast backward
A cutout portion formed in a land portion of the spool to block communication between the penetration-side actuator port and the second flow passage is set to a shape in which an opening area formed between the valve body and the land portion changes in two stages.
2. The control valve according to claim 1, wherein a cutout portion formed in a shoulder portion of the spool to block communication between the penetration-side actuator port and the second flow path is provided in a shape in which a distance between the valve body and a surface of the cutout portion changes in at least two stages.
3. The control valve according to claim 1, wherein the cutout portion formed in the land portion of the spool to block communication of the penetration-side actuator port with the second flow path includes: a first region in which an opening area between the valve body and the shoulder portion is gradually increased; a second region which is provided continuously from the first region and in which an opening area between the valve body and the shoulder portion is fixed; a third region which is provided continuously with the second region and in which an opening area between the valve body and the shoulder portion gradually increases; and a fourth region provided continuously with the third region and having a fixed opening area between the valve body and the shoulder portion,
the distance between the surface of the first region and the surface of the second region and the valve body is set to a first distance, the distance between the surface of the second region and the surface of the third region and the valve body is set to a second distance larger than the first distance, and
the first region and the third region have a semicircular shape in a plan view.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2017/033001 WO2019053799A1 (en) | 2017-09-13 | 2017-09-13 | Control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111032564A true CN111032564A (en) | 2020-04-17 |
Family
ID=65722554
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780093986.3A Pending CN111032564A (en) | 2017-09-13 | 2017-09-13 | Control valve |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US11408520B2 (en) |
| JP (1) | JP6725081B2 (en) |
| CN (1) | CN111032564A (en) |
| DE (1) | DE112017008032T5 (en) |
| WO (1) | WO2019053799A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11680649B2 (en) * | 2020-11-16 | 2023-06-20 | Parker-Hannifin Corporstion | Proportional valve spool with linear flow gain |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001271803A (en) * | 2000-03-27 | 2001-10-05 | Kayaba Ind Co Ltd | Selector valve |
| JP2006071051A (en) * | 2004-09-06 | 2006-03-16 | Komatsu Ltd | Directional control valve |
| WO2009068173A1 (en) * | 2007-11-28 | 2009-06-04 | Robert Bosch Gmbh | Valve arrangement |
| CN103449334A (en) * | 2013-09-05 | 2013-12-18 | 常州大学 | Novel multi-way valve |
| CN204003711U (en) * | 2014-07-11 | 2014-12-10 | 浙江海宏液压科技股份有限公司 | Fork truck collaborates to hoist valve block |
| CN204493327U (en) * | 2015-02-04 | 2015-07-22 | 阜新捷力液压科技有限公司 | Inclined in two-way self-locking multi-way valve |
| CN205064924U (en) * | 2015-09-25 | 2016-03-02 | 比亚迪股份有限公司 | Control valve, multiple unit valve and fork truck |
| JP2016217438A (en) * | 2015-05-19 | 2016-12-22 | 株式会社島津製作所 | Fluid control valve |
Family Cites Families (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3557824A (en) * | 1968-11-01 | 1971-01-26 | Cessna Aircraft Co | Spool control valve |
| US4009864A (en) * | 1975-02-04 | 1977-03-01 | Caterpillar Tractor Co. | Throttling slot configuration for a valve spool |
| US4133510A (en) * | 1977-02-09 | 1979-01-09 | Caterpillar Tractor Co. | Valve spool positioner |
| JPS6054238B2 (en) * | 1977-10-12 | 1985-11-29 | ティー・シー・エム株式会社 | Cargo handling control device for electric cargo handling vehicles |
| DE2902751C2 (en) * | 1979-01-25 | 1981-03-12 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Control valve |
| JPS57195097A (en) * | 1981-05-27 | 1982-11-30 | Nissan Motor | Regulator for speed of reach of reach type forklift |
| JPS5879103A (en) | 1981-11-06 | 1983-05-12 | Mitsubishi Heavy Ind Ltd | Device for detecting amount of deflection of structure |
| JP3158596B2 (en) | 1991-04-15 | 2001-04-23 | 株式会社デンソー | Refrigerator water removal equipment |
| JPH0552451U (en) * | 1991-12-20 | 1993-07-13 | 株式会社島津製作所 | Switching valve |
| JPH08192761A (en) * | 1995-01-17 | 1996-07-30 | Toyota Motor Corp | Fluid passage control valve |
| JP2000053398A (en) | 1998-08-07 | 2000-02-22 | Toyota Autom Loom Works Ltd | Reach control device for reach forklift |
| US6397890B1 (en) * | 1999-02-15 | 2002-06-04 | Case Corp. | Variable metering fluid control valve |
| DE10005290A1 (en) * | 2000-02-07 | 2001-08-09 | Mannesmann Rexroth Ag | Method of manufacturing a valve body |
| US6450194B1 (en) * | 2000-09-26 | 2002-09-17 | Case Corporation | Spool notch geometry for hydraulic spool valve |
| DE10107532A1 (en) * | 2001-02-17 | 2002-08-29 | Mannesmann Rexroth Ag | Directional control valve for load-independent control of a hydraulic consumer with regard to direction and speed |
| KR100496650B1 (en) * | 2002-06-27 | 2005-06-22 | 주식회사 한화 | Flow force compensating spool valve and hydraulic valve, pneumatic valve, three-way control valve, four-way control valve using it |
| JP4719450B2 (en) * | 2004-11-08 | 2011-07-06 | 株式会社豊田自動織機 | Hydraulic control device and hydraulic circuit |
| JP4705445B2 (en) * | 2005-09-27 | 2011-06-22 | サンデン株式会社 | Swing plate compressor |
| JP4900074B2 (en) * | 2007-06-18 | 2012-03-21 | アイシン・エィ・ダブリュ株式会社 | solenoid valve |
| US20140026546A1 (en) * | 2012-07-25 | 2014-01-30 | Caterpillar, Inc. | Regeneration Valve for a Hydraulic Circuit |
| WO2015049728A1 (en) * | 2013-10-01 | 2015-04-09 | 株式会社 島津製作所 | Flow rate control valve |
| EP3201475B1 (en) * | 2014-09-29 | 2018-12-19 | Parker Hannifin Corporation | Directional control valve |
| EP3255284B1 (en) * | 2015-01-08 | 2020-04-01 | Volvo Construction Equipment AB | Flow control valve for construction machine |
| DE102017004531A1 (en) * | 2017-05-11 | 2018-11-15 | Hydac Systems & Services Gmbh | Valve |
-
2017
- 2017-09-13 DE DE112017008032.0T patent/DE112017008032T5/en active Pending
- 2017-09-13 US US16/640,350 patent/US11408520B2/en active Active
- 2017-09-13 JP JP2019541533A patent/JP6725081B2/en active Active
- 2017-09-13 CN CN201780093986.3A patent/CN111032564A/en active Pending
- 2017-09-13 WO PCT/JP2017/033001 patent/WO2019053799A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001271803A (en) * | 2000-03-27 | 2001-10-05 | Kayaba Ind Co Ltd | Selector valve |
| JP2006071051A (en) * | 2004-09-06 | 2006-03-16 | Komatsu Ltd | Directional control valve |
| WO2009068173A1 (en) * | 2007-11-28 | 2009-06-04 | Robert Bosch Gmbh | Valve arrangement |
| CN103449334A (en) * | 2013-09-05 | 2013-12-18 | 常州大学 | Novel multi-way valve |
| CN204003711U (en) * | 2014-07-11 | 2014-12-10 | 浙江海宏液压科技股份有限公司 | Fork truck collaborates to hoist valve block |
| CN204493327U (en) * | 2015-02-04 | 2015-07-22 | 阜新捷力液压科技有限公司 | Inclined in two-way self-locking multi-way valve |
| JP2016217438A (en) * | 2015-05-19 | 2016-12-22 | 株式会社島津製作所 | Fluid control valve |
| CN205064924U (en) * | 2015-09-25 | 2016-03-02 | 比亚迪股份有限公司 | Control valve, multiple unit valve and fork truck |
Non-Patent Citations (1)
| Title |
|---|
| 王晓娟: "节流槽的基本形式", 《小型液压挖掘机多路阀阀芯节流槽研究及应用》 * |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112017008032T5 (en) | 2020-07-02 |
| US11408520B2 (en) | 2022-08-09 |
| JP6725081B2 (en) | 2020-07-15 |
| JPWO2019053799A1 (en) | 2019-12-12 |
| WO2019053799A1 (en) | 2019-03-21 |
| US20200355280A1 (en) | 2020-11-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP6220228B2 (en) | Hydraulic drive system for construction machinery | |
| JP4276646B2 (en) | Hydraulic control valve with regeneration function | |
| EP2123541B1 (en) | Steering system for working vehicle | |
| JP4588089B2 (en) | Fan drive system | |
| CN107850225B (en) | Slide valve, operation device, and work vehicle | |
| CN109563854B (en) | Valve device and fluid pressure system equipped with the same | |
| CN109790857B (en) | Hydraulic drive system for construction machine | |
| JP6282528B2 (en) | Construction machinery | |
| JP2017115992A (en) | Hydraulic system of work machine | |
| JP2011196439A (en) | Hydraulic circuit of turning working vehicle | |
| CN111032564A (en) | Control valve | |
| US11454002B2 (en) | Hydraulic drive system for work machine | |
| EP1961973B1 (en) | Actuator control device | |
| JP4889709B2 (en) | Industrial vehicle hydraulic system | |
| EP1724182A1 (en) | Oil pressure supply device for industrial vehicle | |
| KR20180085784A (en) | Pilot type switching valve | |
| EP3543544B1 (en) | Hydraulic drive device for cargo vehicle | |
| EP0440801B2 (en) | Hydraulic circuit | |
| JP2008018846A (en) | Hydraulic control device for industrial vehicle | |
| JP2020093863A (en) | Hydraulic driving device of forklift | |
| US11053958B2 (en) | Regeneration valve for a hydraulic circuit | |
| JP7392600B2 (en) | Hydraulic control device for industrial vehicles | |
| JP5219880B2 (en) | Hydraulic control system | |
| JP5092550B2 (en) | Hydraulic drive | |
| KR101923017B1 (en) | Hydraulic system for engine anti-stall control |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |